Steam turbine, spur-gear power-box for stoker drives



8 Sheets-Sheet l w ll A. E. WEINGARTNER Original Filed Feb. 21, 1929STEAM TURBINE, SPUR GEAR POWER BOX FOR STOKER DRIVES March 13, 1934.

March 13, 1934. A. E. WEINGARTNER Original Filed Feb. 21, 1929 8Sheets-Sheet 2 March 13, 1934. wEmGARTNER 1,951,002

STEAM TURBINE, SPUR GEAR POWER BOX FOR STOKBR DRIVES Original Filed Feb.21, 1929 8 Sheets-Sheet 3 a Sheets-Sheet 4 urx 1T 5 A. E. WEINGIARTNEROriginal Filed Feb. 21. 1929 STEAM TURBINE, SPUR GEAR POWER BOX FORSTOKER DRIVES March 13, 1934.

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March 13, 1934. A, WEWGARTNER 1,951,002

STEAM TURBINE, SPUR GEAR POWER BOX FOR STOKER DRIVES Original iled Feb.21, 1929 s Sheets-Sheet 5 iilHmi g za March 13, 1934.

STEAM TURBINE A. E. WEINGARTNER 1,951,002

SPUR GEAR POWER BOX FOR STOKER DRIVES Original Filed Feb. 21, 1929 8SheetsSheet 6 flie i I IVES March 13, 1934- A. E. WEINGARTNER STEAMTURBINE, SPUR GEAR POWER BOX FOR STOKER DR Original Filed Feb. 21, 19298 Sheets-Sheet '7 4 2 W 5 m m Z Q IVES March 1934- A. E. WEINGARTNERSTEAM TURBINE, SPUR GEAR POWER BOX FOR STOKER DR Original Filed Feb. 21,1929 8 Sheets-Sheet 8 Maya/"510",

Patented Mar. 13, 1934 UNITED STATES PATENT OFFICE Anthony E.Weingartner, Bethlehem, Pa., as-

signor to American Engineering Company,

Philadelphia, Pa, a corporation of Pennsyl- Vania Original applicationFebruary 21, 1929, Serial No.

341,817. Divided and this application October 28, 1930, Serial No.491,798

9 Claims.

This application is a division of my application for patent filedFebruary 21, 1929, Serial No. 341,817.

My invention relates to power apparatus, and it has for one object theprovision of a powerbox of simple and compact design which isparticularly applicable to stoker structures.

Another object of my invention is to provide a power-box, wherein asteam turbine and a power-transmission system are so combined as to forman exceptionally rigid and non-vibrator structure.

Still another object of my invention is to provide power apparatusparticularly adapted to stoker structures, characterized by therelatively large range in speeds available.

further object of my invention is to provide a steam-driven power-boxrequiring minimum floor space characterized by the fact that the entiredriving system is enclosed, so that no moving parts are visible with theexception of the crank shaft.

A still further object of my invention is to provide a lubricatingsystem adapted to insure a constant supply of clean cool lubricant tothe several bearings, as well as to the pressure control means for theturbine.

A still further object of my invention is to provide an oil-distributionmanifold for the power-box, characterized by the minimum munber of partsrequired, my invention contemplating the forming of the manifold bydrilling a re cess through an enlarged portion of one wall of theoil-chamber section of the power-box housing.

A still further object of my invention is to provide means, whereby oilaccumulating in the chamber portion of the casing containing the chainmay be automatically returned to the main oil reservoir upon themovement of the chain, so that the oil in said reservoir may bemaintained at approximately a constant level.

With these and other objects and applications in view, my inventionfurther consists in the details of construction and operation andarrangement, hereinafter described and claimed and illustrated in theaccompanying drawings, wherein Fig. 1 is a front elevational View of asteamdriven power-box embodying my invention connected to a stokerstructure;

Figs, 2 and 3 are side elevational views of the power-box shown in Fig.1 looking from the left and right, respectively;

Fig. 4 is a top plan view of the power-box of Fig. 1, with the covermember for the pump shown in horizontal section;

Fig. 5 is an enlarged, detail sectional view, taken on the line 55 ofFig. 3;

Fig. 6 is a similar view taken on the line 6-6 of Fig. 3;

Fig. "i is an enlarged, detail vertical sectional view of theoil-cooling means and associated parts, taken on the line 7-4 of Fig. 2;

Fig. 8 is an enlarged view of the cover member for the chain-mechanismsection of the powertransmission system:

Figs. 9 and 10 are longitudinal and transverse vertical sectional viewstaken on the lines 99 and 10--10 of Fig. 8, respectively:

Fig. ll is a detail view of the orbit gears with their associated cam;and

Fig. 12 is an enlarged, detail sectional plan View of the oil-coolingmeans and associated parts, taken on the line 12-12 of Fig. 2.

Referring to the drawings, stoker rams may be connected by rods 2 tocranks 3 of a driven shaft 4. The shaft 4: extends through openingsformed in portions 5 and 6 of spaced side Walls 7 and 8 of a housing 9of a power-box 11, said housing also having front and rear walls 12 and13, respectively.

A relatively large gear-wheel 14 (Fig. 6) is mounted on a portion of theshaft 4 between the side walls 7 and 8, and it meshes with a relativelysmall pinion 15 positioned on a shaft 16 journaled in the side walls 7and 8. The shaft 16 extends through the side Wall 7 and carries on theouter end thereof a hub 17. The hub 17 affords a relatively largegear-wheel 18 a rotatable mounting, and it is connected by means of ashearable pin 19 to a plate 21 secured to the hub 17. The gearing so fardescribed constitutes the low-speed, heavy-duty section of the gearsystem.

The gear-wheel l8 meshes with a pinion 22 formed on a sleeve 23 looselymounted on a horizontally-positioned high-speed shaft 24 extendingparallel to the low-speed crank shaft 4. The tubular sleeve 23 is keyedto a sleeve 25, opposite ends of which are journaled in bearings 26 and27 formed in spaced inwardly-extending flanges 28 and 29, respectively.The flange 28 is integral with the housing 9, while the flange 29 isdetachably secured in an opening 31 formed in the housing 9 and servesto close the same. The sleeve is provided with a pair of arms 32 betweenwhich extend a nonrotatable spindle 33. The spindle 33 afiords a loosemounting for planet gears 34 and 35 of different diameters.

The planet gear 34 meshes with an orbit gear 36 rotatably seated in thehousing 9, while the planet gear 35 meshes with an orbit gear 37similarly mounted in the housing 9. The gears 36 and 37 have theiradjacent edges so recessed as to form shoulders 38 and 39. As shown inFig. 11, a cam 41 is mounted on an inner end 42 of a shaft 43, whichextends outwardly of the housing 9 to an operating handle 44, the cam 43being so positioned between the recessed edges of the orbit gears 36 and37 as to be movable into a gripping engagement with either of saidshoulders 38 and 89, in which position, the cam 43 is also self-locking.When the handle 44 is in the mid or neutral position, the cam 41 is outof engagement with either of the shoulders 38 and 39, permitting thefree movement of the orbit gears 36 and 37.

The planet gear 35 meshes with a gear-wheel 45, formed on the high-speedshaft 24, so that when said shaft is rotated, the planet gears 34 and 35are turned together. Should the operating handle 44be so turned from itsmid-position as to actuate the cam 43 into engagement with the shoulder38, the orbit gear 36 is held stationary and the planet carrier orsleeve 25 is operated at one speed. Should the other orbit gear 37 beheld stationary by an opposite movement of the handle 44, the planetcarrier 25 is rotated ata different speed. Thus the speed of thehigh-speed gear section, which extends from the driving pinion orgear-wheel 45 to the gearwheel 18, is controlled with these gearspermanently in mesh. For a further description of certain of the detailfeatures of the high and low-speed gear sections, reference is made tomy Patent No. 1,889,718, patented November 29, 1932, and assigned to theAmerican Engineering Company.

My invention further contemplates the provision of means, whereby thehigh-speed shaft 24 may be driven by steam rather than by electricalmeans, thereby affording a large range in speed variation, say, from 10to 1. To this end, broad- 1y, I mount a steam turbine 46 of conventionaldesign on an upper portion 47 of the housing 9 which extends above thehigh-speed shaft 24, as shown in Fig. 1 and then connect a shaft 48 ofthe turbine by gear and chain systems 49 and 51 to the high-speed shaft24, as illustrated in Fig. 5.

More specifically, an upper end portion 52 of the housing section 47 isprovided with apertures 53 and 54 in spaced side walls 55 and. 56thereof. A housing 57 of the turbine is provided with a tubularextension 58, which closely fits the apertures 53 and. 54, as well as apcripheral flange 59 which may be bolted or otherwise secured to theside wall 55. Bearings 61 and 62 are respectively positioned in thetubular end portions 63 and 64 of the housing projection 58, whereby anextended portion 65 of the turbine shaft 48 may be rotatably supportedin position. Such method of supporting the turbine46 in the housing 9assures a rigid, non vibratory connection therebetween. The mounting ofthe turbine 46 on the side of the housing 9, so that the turbine shaft48 is parallel to the high-speed shaft 24 results in an exceedinglycompact unit, occupying a minimum amount of floor space and affordingmaximum accessibility to the principal portions of the power-box.

bolts or 1 other means.

top and bottom walls and 76 (Fig. 3) and a curved end wall 77. The wall69 is extended above the upper open sides of the chambers 66 and 67 toprovide an upper portion 78. The

portion 78 is provided with an opening 79 adapted to receive an outerend portion 81 of the extension portion 58 of the turbine housing 57,the end portion '81 being prevented from turning in the aperture 79 bymeans of locking means 82, and by the securing means of flange 59.

The portion 78 is also provided with a flange 83 which abuts against theside 56 of the housing portion 47 and may be secured thereto by Thelower portion of the wall 69 is provided with a flange 84, which ispositioned in abutting relation with the side 56 of the housing portion47 and which is connected with the upper flange 83. Thus, a cham- I ber85 is formed between the side wall 56 and the side wall 69 which ispositioned below the turbine shaft extension 48.

The gear system 49 comprises a driving pinion 86, which is mounted on anoverhanging end portion 87 of the turbine shaft extension 48 and whichmeshes with a relatively large gearwheel 88 keyed on an inner endportion of a tubular shaft 89. The shaft 89 is rotatably mounted on itsinner and outer ends on antifriction devices 91 and 92 respectivelycarried on eccentric portions 93 and 94 of a jack shaft End portions 96and 97 of the jack shaft are journaled respectively in apertures 98 and99 positioned intermediate the upper and lower ends of wall 69 andimmediately adjacent to horizontal upper edge portion 101 of wall 74.

An outer end portion 102 (Fig. 3) of the jack shaft 95 is provided withan arm 103 having at one end micrometer-adjusting means 104, whereby thejack shaft 95 may be turned through a predetermined angle. Themicrometer adjusting means 104 comprises a pair of oppositely-positionedset screws 105 and 106 which extend into an enlarged opening 107 in theouter end of the arm 103. A stationary bolt 108 extends from the casing68 between the ad jacent inner ends of the set screws 105 and 106 andconstitutes an abutment therefor. When it is desired to impart apredetermined angular movement to the jack shaft 95, one of the setscrews 105, 106 is loosened while the other is tightened. When the jackshaft 95 is turned in this manner, the position of the rotatable shaft89 and hence that of the gear-wheel 88 is adjusted bodily relative tothe pinion 86. Thus, the distance between the intermediate tubular shaft89 andthe turbine shaft 48 may be varied, thereby insuring the propermeshing of the gear-wheel 88 with the driving pinion 86.

The chain system 51 comprises a sprocketwheel 109 which is mounted on anouter end of the intermediate tubular shaft 89 in the chamber 67 betweenthe walls 71 and 74. The sprocket-wheel 109 is connected by means of achain 111 with a second sprocket-wheel 112 mounted on an outer endportion 113 of the high-speed shaft 24 which extends through openings114 and 115 in the opposite walls 71 and 74 of the chamber 67. Shouldslack occur in the chain 111, this may be compensated by properlyturning the set screws 165 and 106 of the micrometer-adjusting means104. The gear and chain transmission systems 49 and 51 thus aiford aneasily adjustable and flexible connection between the turbine shaft andthe high-speed shaft 24.

As shown in Fig. 5, the opening 114 in the side wall 71 is closed bymeans of a circular plate 116 which is secured to the adjacent portionof the casing wall 71, as well as to the closure plate 29. The opening115 is closed by means of a member 117 which is provided with a bearing118 for the outer end portion of the high-speed shaft extension 113.

My invention further embodies a simple and efficient system oflubrication for the various bearings of the power-box, the upper housingportion 47 being so formed as to provide a chamber or reservoir 119which extends from a lower wall 121 thereof upwardly between side walls55 and 56 to an upper wall 122 positioned just above the extension. 58of the turbine housing 57. The chamber 119 is preferably filled with oilor other lubricating material to a level indicated at 123.

A lower portion 124 of the side wall 56 is provided with a series ofapertures 125, extending across the width thereof, which are positionedjust below the upper level 123, permitting oil to pass from the chamber119 into the chamber 85. The chamber is connected to the chamber 66 ofthe casing 68 by means of a plurality of apertures 126, so that oil isalso present in the chamber 66. The passage of oil from the chamber 66to the chamber 67 is prevented by means of a cover member 127, whichencloses the upper side of the chamber 67 and which is mounted on theupper horizontal edges 101 of the walls 71 and 74. Packing 128 ispositioned between the wall 71, the cap 127 and the rotatable tubularshaft 89, so as to prevent other than a predetermined limited passage ofoil into the chamber 67 at this point, such as is necessary forlubrication.

The accumulation of oil in the chamber 67 is prevented by means of thedevice shown in Figs. 5, 8, 9 and 10, wherein it will be noted that acurved plate 129 has an outer end portion 130 supported on a pin 131extending between side walls 132 of the cover member or cap 127. Anintermediate portion 133 of the plate 129 is slightly curved andprovided with an aperture 134, one edge 135 of which is beveled to forma scraping edge, as shown in Fig. 9, and positioned just above a topportion 136 of the chain system 51, so that a portion of the oil carriedupwardly by the chain 111 is removed therefrom and not returned again tothe base portion of the chamber 67. The oil thus removed fiows over adownwardly-inclined rear portion 137 of the plate 129 into a tubularbase portion 138.

Opposite ends 139 and 141 (Fig. 10) of the tubular portion 138 of theplate 129 are provided with inwardly-extending flange portions 142 and143 which closely fit a pipe 144. The pipe 144 is supported in andextended through the opposite side walls 132 of the cover member 127.The oil flowing down the plate portion 137 accumulates in a recess 145between an intermediate portion 146 of the pipe 144 and the tubularplate portion 138. The intermediate portion 146 is provided with aplurality of apertures 147, so that the oil may readily pass into thepipe 144. The ends of the pipe 144 open into the casing 68, the innerend opening directly into the chamber 66, permitting the oil passingtherefrom to drain back into the chamber 66.

An upper edge 147a of the tubular portion 138 is extended upwardlytoward the free end 130 of the plate 129 by means of a plate portion148, thereby forming with the rear end portion 137 a chamber 149 inwhich the oil may accumulate in the event that it does not immediatelydrain through the discharge pipe 144. An end 151 of the bent-back wallportion 148 is somewhat resilient and engages an upper side 152 of thecap member 127, whereby the plate 129 may be resiliently held inposition. Should such oilcollecting means not be used in the chamber 67,the oil would not only accumulate therein to an undesirable extent, butdiihculty would also be had in maintaining the proper oil level in themain reservoir 119.

An oil pump 153 of conventional design may be bolted on a front portion154 of the cover member 127, and it is driven by means of chainmechanism 155. The mechanism 155 comprises a sprocket-wheel 156, whichis secured on the tubular shaft 89 between the gear-wheel 49 and thewall 71, a connecting chain 157, and a second sprocket-wheel 158. Thesprocket-wheel 158 is mounted on an upper end of a shaft 159 of the pump153.

The lubrication of the gear system 49, as well as the chain mechanism155, is accomplished by means of a rotary plate 160 (Fig. 5) which ismounted on the turbine-shaft end portion 87 just beyond the drive gear86. The rotary plate 160 is of such diameter as to extend beyond themeshing point of the gear-wheels 49 and 86 so as to be in the path oftravel of the oil which is forced from between these two gears wheels.The oil striking the rotary plate 160 is thrown outwardly by centrifugalforce, thereby assuring a proper lubrication of adjacent rotary parts.The lubrication of these parts may also be effected by means of a pipe161 carrying oil under pressure from the pump 153,'as shown in Fig. 1.

As shown in Figs. 1, 3, 4 and 5, the oil thrown by the rotary plate 160is confined to the space immediately adjacent to the chamber 66 by meansof a cover member or housing 162 which encloses the open upper side ofthe chamber 66, the cover member 127 for the chamber 67, the pump 153,the gear system 49 and the pumpdriving mechanism 155. An inner endportion 163 of the housing 162 abuts against the outer surface of theside Wall 69 and its extended portion 78, while lower edge portions 164are mounted on the upper horizontal edges 101 of the casing 68. An outerend of the cover member 162 is provided with an opening 165 and aremovable closure plate 166, whereby access may be had to the partswithin the cover member 162. Y

The pump 153 is provided with suction and discharge pipes 167 and 168which extend therefrom downwardly through apertures 169 and 171 in therear end portion of the cover plate 127. The suction and discharge pipes167 and 168 are then extended outwardly of the powerbox through theopenings 172 and 173 formed in the rear wall portion of the chamber 67.The suction pipe 167 terminates in the valve plate 174 positioned on theside wall 55 immediately adjacent to the base portion of the oil chamber119.

The valve plate 174 (Figs. 2, 5 and 7) is provided with a verticalpassage 175 in communication with the suction pipe 167. The passage 175is provided with a restricted portion forming a seat 176 for a ballvalve 177 adapted to prevent a reverse flow of the oil through thesuction pipe 167 thereby insuring a constant supply of oil in thesuction pipe 167. The portion of the passage 1'75 beyond the valve 177is connected to a suction pipe 178, which extends through the adjacentportion of the wall 55 into the bottom portion of the oil chamber 119,and it is provided with a plurality of slotted openings 179. In orderthat the oil may be cooled, a tubular cooling coil 180 is positioned inthe lower portion of the chamber 119 so as to surround the suction pipe178. Opposite ends 181 and 182 of the coil 180 extend through the Wall55- and openings 183 and 184 in the valve plate 174, respectively, andare connected by pipes 185 to a cooling system (not shown).

The cooling coil 189, as well as the suction pipe 178, are enclosed bymeans of a tubular screen 186 which extends outwardly from the valveplate 174, whereby only clean oil may be supplied to the suction pipe178. A supporting rod 187 extends inwardly from the valve plate 174 justbelow the upper side of the cooling coil 180, so that the latter may berigidly secured in position. The cooling coil 180, the screen 186, thesuction pipe 178, and the valve plate 174 thus constitute the removableunit which may be easily detached from the powerbox for purposes ofreplacement or repair.

The pressure pipe 168 is provided with a section 188 positionedexteriorly of the power-box and a section 189 which extends through theoil chamber 119, just below the turbine extension 58, between the frontand rear walls 12 and 13, respectively, of the power-box housing 9. Inaccordance with my invention, the pipe section 189 is core cast.

A still further feature of my invention is the provision of adistributing manifold 191 in the upper front wall portion of the housingsection 47, comprising an aperture 192 which is drilled horizontally ina tubular housing portion 193. 'Ihe formation of the manifold 191 of anintegral portion of the housing 9 permits the elimination of thenumerous pipes and fittings characteristic of such structures. One end194 of the aperture or boring 192 is closed by means of a plug 195,while an opposite end 196, is connected by means of a pipe 197 to agovernor 198 for the turbine 46.

The manifold 191 is also connected by passages 199 and 201 to the spacedbearings 61 and 62 for the turbine-shaft extension 48. A safety valve202 is also connected to the manifold 191. A by-pass valve 203 isconnected to the manifold 191 and to the oil chamber 119, whereby thepressure of the oil in the manifold 191 may be controlled The governor198 for the turbine 46 is so designed that when the by-pass valve 203 isfully opened, the speed of the turbine 46 is a maximum, but that whenthe valve 203 is fully closed, the speed of the turbine 46 is a minimum,thereby providing desired range in speed variation of the turbine shaft48.

In operation, assuming the turbine is supplied with steam through a pipe204 and the control valve 293 fully closed, the speed of the turbine isa minimum. If the control lever 44 is now moved to the right of itsmid-position, the orbit gear 37 is locked, resulting in the relativelyslow movement of the gear system connecting the high-speed shaft 24 andthe stoker shaft 4. Should the lever 44 be moved in the oppositedirection from its mid-position, the orbit gear 36 is held stationary,so that the operating speed of the shaft 4 is slightly increased. Shouldit be desired to operate the shaft 4 at an increased speed, the by-passvalve 203 is opened slightly, permitting the turbine 46 to operate at ahigher rate of speed. The speed of the shaft 4 may now be adjusted aboveor below that determined by the turbine 46 merely by moving the handle44 to the right or left.

The operation of the turbine-driven intermediate shaft 89 through thechain system 155 causes the turning of the pump 153, with the resultthat cooled lubricating oil is drawn from the main oil reservoir 119through the screen 186 into the suction pipe 178, and is finallydistributed to the various parts of the power-box from the manifold 191.Such oil as passes into the chamber 67 around the packing 128 isreturned to the chamber 66 and out into the main reservoir 119 throughthe openings 125 and 126, by means of the oil-collector deviceimmediately below the cover member 127.

While I have shown only one embodiment of my invention, for the purposeof describing the same and illustrating its principles of constructionand operation, it is apparent that various changes and modifications maybe made therein, without departing from the spirit of my invention. Idesire, therefore, that only such limitations shall be imposed thereon,as are indicated in the appended claims or as are demanded by the priorart.

I claim:

1. In combination, a rotary member provided with a material on theperiphery thereof, a plate provided with an opening forming a scrapingedge, supporting means for one end portion of said plate, and a tubularsupporting member for another portion of said plate, said tubularsupporting member being provided with apertures adapted to receive fluidremoved by said scraping edge from said rotary member, said plate havinga bent-back portion adapted to engage a stop, so that said plate may beheld in position.

2. In power drive mechanism, the combination with a drive shaft, of asecond shaft, and transmission elements operatively connecting saidshafts, a fluid pump, transmission means operatively connecting saidfluid pump with the second shaft, a housing in which said shafts arejournaled, said housing having separate chambers, one of whichconstitutes a reservoir for lubricant and another of which embraces saidtransmission mechanisms and the pump, means providing communicationbetween said chambers whereby a portion of said transmission mechanismis immersed in said lubricant, means providing for lubrication of saidtransmission mechanisms and the bearings of the said second shaft bylubricant entrained by the transmission mechanism, means connecting thesuction side of said pump with the body of lubricant in said reservoir,and ducts connecting the discharge of said pump with the bearings of thedrive shaft.

8. In power drive mechanism, the combination with a drive shaft, of asecond shaft, and transmission elements operatively connecting saidshafts, a fluid pump, transmission means operatively connecting saidfluid pump with the sec- 0nd shaft, a housing in which said shafts arejournaled, said housing having separate chambers, one of whichconstitutes a reservoir for lubricant and another of which embraces saidtransmission mechanisms and the pump, means providing communicationbetween said chambers whereby a portion of said transmission mechanismis immersed in said lubricant, means providing for lubrication of saidtransmission mechanisms and the bearings of the said second shaft bylubricant entrained by the transmission mechanism, means connecting thesuction side of said. pump with the body of lubricant in said reservoirand the discharge side of said pump with the bearings of the driveshaft, and means for cooling the lubricant withdrawn by said pump fromthe reservoir.

i. In power drive mechanism, the combination with a drive shaft, of asecond shaft, and transmission elements connecting said shafts, a fluidpump, transmission mechanism connecting said pump with said secondshaft, a motor connected with said drive shaft, a housing for saidmechanism, said housing having a chamber constituting a reservoir for alubricant, means connecting the suction side of said pump with the bodyof lubricant in said reservoir and the discharge of said pump with thevarious parts of said mechanism requiring lubrication, a fluidpressure-regulated governor for said motor, means for operativelyconnecting said governor with the pump, and a valve-controlled bypassfrom said connection to the reservoir whereby the pressure applied bysaid pump to the governor may be regulated.

5. In power drive mechanism, the combination with a drive shaft, andtransmission mechanism connected therewith, of a motor for driving saidshaft, a housing for said shaft and mechanism, said housing including areservoir for a lubricant, a pump operatively connected with said shaft,a fluid pressure-controlled governor for said motor, a manifold, andmeans connecting the pump with the reservoir and said manifold wherebylubricant may be supplied to the latter under pressure, lubricatingducts extending to parts of said mechanism from said manifold, means forconnecting the manifold to said governor, and a valve-controlled bypasseXtending from said manifold to the reservoir for regulating the fluidpressure applied to the gover nor.

6. In power drive mechanism, the combination with a drive shaft, of adriven shaft, an intermediate shaft, and transmission mechanismsrespectively connecting the drive shaft with the intermediate shaft andthe intermediate shaft with the driven shaft, a housing for said drivemechanism comprising separate chambers, one of which constitutes areservoir for a lubricant, a second of which embraces the transmissionmechanism connecting the drive shaft with the intermediate shaft, and athird embracing the transmission mechanism connecting the intermediateshaft with the driven shaft, means for establishing communicationbetween the first and second-named chambers whereby the lubricant in thereservoir is made available for lubrication of the first-namedtransmission mechanism, means permitting a limited flow of lubricantfrom said second chamber to the third chamber for lubricating thetransmission mechanism therein, means for returning lubricant from saidthird chamber to the reservoir to thereby prevent accumulations ofiubricant in said chamber, a pump cperatively connected with said driveshaft and with said reservoir, and means for directing lubricantwithdrawn by said pump from the reservoir to the bearings of said driveshaft.

'7. In power drive mechanism, the combination with a drive shaft and adriven shaft, of an intermediate shaft, and transmission mechanismsoperatively connecting the drive shaft with the intermediate shaft andthe intermediate shaft with the driven shaft respectively, a housing forsaid drive mechanism comprising chambers respectively enclosing saidtransmission mechanisms, means for admitting lubricant to thefirst-named chamber to afford a lubrication of the transmissionmechanism connecting the drive shaft with the intermediate shaft, meansfor permitting a limited flow of iubricant from the first chamber to thesecond chamber for lubricating the transmission mechanism connecting theintermediate shaft with the driven shaft, and means for returninglubricant from the second chamber to the first to prevent accumuiationof lubricant in the second chamher.

8. in power drive mechanism, the combination with a pair of shafts, andtransmission mechanism connecting said shafts, of a housing having achamber embracing said transmission mechanism and comprising also asecond chamber constituting a reservoir for a lubricant, means foradmitting lubricant from said reservoir to the first-named chamber tolubricate said transmission mechanism, and means operatively associatedwith said transmission mechanism for returning excess lubricant from thefirst-named chamber to the reservoir, said last mentioned meansincluding a member for removing at least a portion of the lubricantadhering to said transmission mechanism.

9. In power drive mechanism, the combination with a drive shaft, of adriven shaft, a gear on said driven shaft, and a pinion on said driveshaft meshing with said gear, a fluid pump, and transmission mechanismoperatively connecting the pump with the driven shaft, a housing inwhich said shafts are journaled, said housing having alubricant-containing chamber embracing the lower portion of said gear, asplash plate mounted on the drive shaft adjacent said pinion position toreceive lubricant forced transversely from between the intermeshingteeth of said gear and pinion and adapted to project said lubricant bycentrifugal action onto said transmission, and means for connecting thepump with the body of lubricantin the reservoir and with the bearings ofsaid drive shaft whereby lubricant withdrawn from the reservoir isdirected to said bearing ANTHONY E. WEINGARTNER.

